EP1905965A2 - Vorspannungsfederachse für einen Nockenwellenversteller - Google Patents

Vorspannungsfederachse für einen Nockenwellenversteller Download PDF

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Publication number
EP1905965A2
EP1905965A2 EP07117090A EP07117090A EP1905965A2 EP 1905965 A2 EP1905965 A2 EP 1905965A2 EP 07117090 A EP07117090 A EP 07117090A EP 07117090 A EP07117090 A EP 07117090A EP 1905965 A2 EP1905965 A2 EP 1905965A2
Authority
EP
European Patent Office
Prior art keywords
spring
coil
arbor
radius
innermost
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07117090A
Other languages
English (en)
French (fr)
Other versions
EP1905965A3 (de
Inventor
Thomas H. Lichti
Michael J. Fox
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Delphi Technologies Inc filed Critical Delphi Technologies Inc
Publication of EP1905965A2 publication Critical patent/EP1905965A2/de
Publication of EP1905965A3 publication Critical patent/EP1905965A3/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34479—Sealing of phaser devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs

Definitions

  • the present invention relates to a camshaft phaser for controlling the phase relationship between the crankshaft and a camshaft of an internal combustion engine; more particularly, to a vane-type phaser having a torsion spring for biasing the rotor toward an extreme position; and most particularly, to a phaser having an improved bias spring arbor for minimizing spring stress and hysteresis.
  • Camshaft phasers for varying the phase relationship between the pistons and the valves of an internal combustion engine are well known.
  • Some prior art camshaft phasers include a torsion bias spring to bias the rotor toward an extreme rotational position.
  • a torsion bias spring to bias the rotor toward an extreme rotational position.
  • such a spring is accommodated on an arbor within a well within the rotor hub.
  • Others may reside on the outside of the stator cover around the arbor.
  • a torsion spring changes diameter as it is torsionally deflected. Further, in loading such a spring, moments are inherently applied to the spring which must be counteracted in the restraint of the end coils, which twisting moments also act to distort and shift the body of the spring away from the central axis of the spring and the phaser. Further, such a spring requires radial clearance in the well, typically between about 5% and about 10% of the spring rest diameter, to allow the spring to move freely.
  • a torque bias coil spring for a camshaft phaser is disposed around a central arbor for supporting the spring.
  • the radii of the arbor is such that the spring has operating clearance of 5-10%, as in the prior art.
  • the arbor includes regions of higher radius at the arbor ends supporting the innermost and outermost coils of the spring. These regions serve to prevent the spring from being laterally displaced during torsional motion, thus minimizing the relative motion at the spring contact points, reducing stress on the spring, and improving the efficiency of the spring by reducing frictional hysteresis.
  • a prior art camshaft phaser 10 includes a stator 12 driven by a sprocket wheel 14 that is bolted to a front cover 16 by bolts 18.
  • a rotor 20 is disposed for rotation within stator 12 for attachment to an engine camshaft (not shown) to vary the timing of valves in an associated internal combustion engine 22 as is well known in the art and need not be elaborated upon here.
  • Rotor 20 includes an annular central well 24 surrounding a central arbor 26, defining an annular chamber 27 therebetween.
  • a torsional coil spring 28 is disposed in chamber 27 for biasing rotor 20 into an extreme rotational position, typically a position wherein the valve overlap is minimized, at predetermined modes of operation such as engine shutdown and startup. In the cross-sectional view shown in FIG. 1, only the innermost coil 28a of spring 28 is visible.
  • a radial spring tang 30 engages a slot 31 in rotor 20 to urge the rotor in a clockwise direction with respect to stator 12.
  • Spring 28 is captured under torsional stress between rotor 20 and cover 16 during assembly of phaser 10. As noted above, such torsional stress causes a deformation of spring 28, creating contact points between the spring coils and the walls of the annular well and the arbor.
  • open triangle 34 and open diamond 36 indicate first and second contact points, respectively, of innermost spring coil 28a with slot 31 and well 24, which contact restrains the torsional moment of the spring.
  • Solid arrow 38 shows the lateral displacement of the spring against arbor 26.
  • the first contact point at open triangle 34 is obvious.
  • the body of spring 28 moves off center in this direction, as indicated by arrow 38.
  • the second contact point at open diamond 36 typically occurs approximately 3 ⁇ 4 of a turn from tang 30, as shown. Due to the contact occurring 3 ⁇ 4 of a turn into the active coils, there is relative motion and thus friction occurring at this contact, which increases the frictional hysteresis of the torsional spring load. Note that the diameter of arbor 26 could be increased to change the second contact point to 1 ⁇ 4 of a turn, near arrow 38, but this would provide insufficient operating clearance for the spring, effectively binding the spring as it tightens down on the arbor during deflection (spring diameter decreases). This would cause additional increases in frictional hysteresis.
  • the first contact occurs at tangential tang 32 in slot 33.
  • the direction of this force causes outermost coil 28x to shift off-center in the direction shown by solid arrow 42. (Note that cover 16 overhangs spring coil 28x in this area to keep the spring axially constrained.)
  • the second deformation contact again occurs at about 1 ⁇ 4 of a turn, and as much as approximately 1 ⁇ 2 of a turn, from tang 32, indicated by open diamond 44.
  • the radial shifting of the position of the two ends 30,32 of the spring causes friction and wear, and creates difficulties in configuring other parts of the phaser within the given phaser diameter.
  • the fact that the secondary contacts occur at about 1 ⁇ 4 of a turn, and as much as approximately 1 ⁇ 2 of a turn, into the body of the spring effectively eliminates those positions of the spring from participating; thus, the spring behaves as though it had fewer coils. Therefore, the observed spring rate is not as low as intended, and the observed load deflection curve includes a large amount of frictional hysteresis.
  • phaser 110 is similar in most respects to prior art phaser 10. Several redundant part numbers are omitted for clarity of presentation but should be assumed.
  • rotor 20 includes an annular well 24 surrounding an improved central arbor 126.
  • Torsional coil spring 28 is disposed in well 24 and is connected to rotor 20 and cover 16 as in the
  • Improved arbor 126 provides the recommended 5% to 10% operating clearance to spring 28 as in the prior art, over the middle coils of the spring, at a radius 164 exemplary of the prior art arbor radius.
  • arbor 126 is provided with a larger diameter angular region 160 having a radius 162 substantially equal to (but slightly less than, to permit assembly of the spring onto the arbor) the inner radius 129 of spring 28.
  • Radius 162 thus is greater than the radius 164 of the intermediate portion of the arbor adjacent the intermediate spring coils between the innermost and outermost coils.
  • Angular region 160 thus becomes the de facto inner bearing surface for spring 28 during rotation of the spring about the arbor with the rotor 20 and the cover 16 at the innermost and outermost spring ends, respectively.
  • the radial deformation of the spring seen at arrows 38,42 in FIGS. 1 and 2, is essentially eliminated by regions 160 at corresponding arrows 138,142 and open diamonds 136,144 in FIGS. 3 and 4.
  • the present invention radially constrains end coils 28a,28x in a manner to avoid frictional contacts beyond the first 1 ⁇ 4 turn at both spring ends, which minimizes frictional losses and functionally adds nearly a full turn to the spring. Also, the coils are supported in a manner to keep the deflected coil diameter centered on the phaser axis 146 during actuation of the phaser and minimizes phaser contact with the remainder of the coils.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Springs (AREA)
EP07117090A 2006-09-29 2007-09-24 Vorspannungsfederachse für einen Nockenwellenversteller Withdrawn EP1905965A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/540,152 US7614372B2 (en) 2006-09-29 2006-09-29 Bias spring arbor for a camshaft phaser

Publications (2)

Publication Number Publication Date
EP1905965A2 true EP1905965A2 (de) 2008-04-02
EP1905965A3 EP1905965A3 (de) 2009-12-02

Family

ID=38961886

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07117090A Withdrawn EP1905965A3 (de) 2006-09-29 2007-09-24 Vorspannungsfederachse für einen Nockenwellenversteller

Country Status (3)

Country Link
US (1) US7614372B2 (de)
EP (1) EP1905965A3 (de)
JP (1) JP2008088979A (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015067250A1 (de) * 2013-11-11 2015-05-14 Schaeffler Technologies AG & Co. KG Nockenwellenversteller

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010063706A1 (de) 2010-12-21 2012-06-21 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller mit Rückstellfeder
US9103239B2 (en) 2011-12-27 2015-08-11 Aisin Seiki Kabushiki Kaisha Valve opening-closing timing control device and method for attaching front member thereof
JP6443279B2 (ja) * 2015-09-11 2018-12-26 株式会社デンソー バルブタイミング調整装置
US10611406B2 (en) * 2018-05-31 2020-04-07 Deere & Company Rotary position sensor isolator
CN108728671B (zh) * 2018-08-31 2024-05-31 江西海汇龙洲锂业有限公司 一种便于锂云母提锂浸取固体物料的搅洗装置

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993024736A1 (de) * 1992-06-01 1993-12-09 Ina Wälzlager Schaeffler Kg Vorrichtung zur kontinuierlichen winkelverstellung zwischen zwei in antriebsverbindung stehenden wellen
US20010003974A1 (en) * 1999-12-15 2001-06-21 Shuji Mizutani Valve timing adjuster for internal combustion engine
US20030177993A1 (en) * 2002-02-28 2003-09-25 Aisin Seiki Kabushiki Kaisha Variable valve timing device
US20040182342A1 (en) * 2002-12-24 2004-09-23 Aisin Seiki Kabushiki Kaisha Variable valve timing control device
US20050115526A1 (en) * 2003-10-28 2005-06-02 Hydraulik-Ring Gmbh Camshaft Adjusting Device for Vehicles, Especially Motor Vehicles
WO2006035602A1 (ja) * 2004-09-28 2006-04-06 Aisin Seiki Kabushiki Kaisha 弁開閉時期制御装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6311654B1 (en) * 1998-07-29 2001-11-06 Denso Corporation Valve timing adjusting device
US6276321B1 (en) * 2000-01-11 2001-08-21 Delphi Technologies, Inc. Cam phaser having a torsional bias spring to offset retarding force of camshaft friction

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993024736A1 (de) * 1992-06-01 1993-12-09 Ina Wälzlager Schaeffler Kg Vorrichtung zur kontinuierlichen winkelverstellung zwischen zwei in antriebsverbindung stehenden wellen
US20010003974A1 (en) * 1999-12-15 2001-06-21 Shuji Mizutani Valve timing adjuster for internal combustion engine
US20030177993A1 (en) * 2002-02-28 2003-09-25 Aisin Seiki Kabushiki Kaisha Variable valve timing device
US20040182342A1 (en) * 2002-12-24 2004-09-23 Aisin Seiki Kabushiki Kaisha Variable valve timing control device
US20050115526A1 (en) * 2003-10-28 2005-06-02 Hydraulik-Ring Gmbh Camshaft Adjusting Device for Vehicles, Especially Motor Vehicles
WO2006035602A1 (ja) * 2004-09-28 2006-04-06 Aisin Seiki Kabushiki Kaisha 弁開閉時期制御装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015067250A1 (de) * 2013-11-11 2015-05-14 Schaeffler Technologies AG & Co. KG Nockenwellenversteller

Also Published As

Publication number Publication date
US20080078343A1 (en) 2008-04-03
JP2008088979A (ja) 2008-04-17
EP1905965A3 (de) 2009-12-02
US7614372B2 (en) 2009-11-10

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